US3885936A - Heat exchangers - Google Patents

Heat exchangers Download PDF

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Publication number
US3885936A
US3885936A US334215A US33421573A US3885936A US 3885936 A US3885936 A US 3885936A US 334215 A US334215 A US 334215A US 33421573 A US33421573 A US 33421573A US 3885936 A US3885936 A US 3885936A
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United States
Prior art keywords
tubes
heat exchanger
tube
fluid
parallel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US334215A
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English (en)
Inventor
Gerald John Nicholson Limebeer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LUND BASIL GILBERT ALFRED
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Individual
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Filing date
Publication date
Priority claimed from ZA721381A external-priority patent/ZA721381B/xx
Application filed by Individual filed Critical Individual
Priority to US05/535,342 priority Critical patent/US3969448A/en
Application granted granted Critical
Publication of US3885936A publication Critical patent/US3885936A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
    • F28D5/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material
    • F28F21/067—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • F28F9/0132—Auxiliary supports for elements for tubes or tube-assemblies formed by slats, tie-rods, articulated or expandable rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/04—Arrangements for sealing elements into header boxes or end plates
    • F28F9/06—Arrangements for sealing elements into header boxes or end plates by dismountable joints
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/02—Streamline-shaped elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/20—Fastening; Joining with threaded elements
    • F28F2275/205—Fastening; Joining with threaded elements with of tie-rods
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/90—Cooling towers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S261/00—Gas and liquid contact apparatus
    • Y10S261/11—Cooling towers

Definitions

  • the ratio of [58] Field of Search 165/172, l5], 79; 62/304; width to length of these passages is between 0.3 and 26l/Dlfi 11 1.0.
  • the tubes are spaced apart at various levels by means of inclined spacers.
  • Referen e Cited water may be fed around them from a launder via 2 UNITED STATES PATENTS system of spacers. The spacers lower down serve to redistribute the water running down the flanks of the tubes.
  • the invention further provides that the tubes are so shaped and positioned that any passage formed where two adjacent tubes are at their closest to one another has a ratio of width between the tubes and length in the direction of flow of the second fluid of between 0.3 and
  • the invention thus far outlined leads to an improved pressure drop efficiency factor and is concerned with the sensible heat transfer between the fluid in the tube and the gas flowing past.
  • such augmenting is achieved by arranging the planes of symmetry of the tubes to be substantially vertical and providing means for applying a liquid to the top of the exterior surfaces of the tubes for a continuous film of the liquid to form at least on the flanks of each tube.
  • the heat exchanger further includes a channel parallel to the top spacer, an overflow weir along one edge of the channel and an apron from the weir to the top spacer. Series of these spacers are also positioned at suitable intervals down the lengths of the tubes to effect redistribution of liquid running down the tubes.
  • FIG. 1 is a vertical section through the top of a heat exchanger according to the invention
  • FIG. 2 is a similar view further down the heat exchanger
  • FIG. 3 is again a similar view of the heat exchanger just above the bottom tube sheet
  • FIG. 4 is a plan view on the line 4-4 of FIG. I,
  • FIG. 6 is a fragmentary view of a form of heat exchanger tube.
  • FIG. 1 is a section through the top tube sheet of a heat exchanger and should be read in conjunction with FIG. 4.
  • Each tube is positioned with its plane of symmetry or the chord plane of its aerofoil section in the direction of air flow.
  • the plane of symmetry is thus at right angles to the aperture plane of the heat exchanger.
  • the arrow A indicates the direction of air flow.
  • the tubes 7 extend between tube sheets at the top and the bottom. Each tube sheet is the inverse of the other except for a difference to be pointed out later on.
  • the top tube sheet is illustrated in FIGS. 1 and 4 while part of the lower tube sheet is illustrated in FIG. 3.
  • the ends of the tubes 7 are assembled with the aid of strips cut from stiff extruded sheets of plastics.
  • FIG. 4 there are three kinds of strips 8, 9 and 10.
  • the strips are extruded in a direction normal to the paper in FIG. 4 and cut to provide strips as shown in FIG. 1.
  • the strips 8 are formed to accommodate the noses of leading tubes, the strips 9 accommodate at one side the tails of the tubes and at the other side the noses of the tubes. while the strips 10 accommodate the cusps of the trailing row of tubes.
  • the top layer of strips is covered with a neoprene seal 15 (FIG. I).
  • top tube sheet there are a series of spacer strips similar to those in the tube sheet, but with inclined top surfaces.
  • the spacer strips -26 are placed at suitably stepped vertical intervals.
  • a feed trough 17 with an apron 18 leads water on to the top strip 20.
  • the water cascades down until the strip 26 is reached.
  • the latter has a slope opposite to the other strips.
  • the strips 20-26 are spaced vertically so as to allow water to escape between them in the direction of the air current. Thus films of water are caused to gravitate down the flanks of the tubes 7.
  • Secondary tie rode 19 between strong backs 27 and an angle iron 28 serve to clamp the assembly together.
  • a heat exchanger of the inven tion will in practice be as tall as l5 metres.
  • additional spacers 30 are provided at intervals of 1.75 me tres or so down the heat exchanger.
  • further secondary tie rods 19 and strong backs 27 are provided in the zone of these redistribution spacers 30.
  • Such a zone is illustrated in FIG. 2.
  • the heat exchanger thus far described can be used for sensible heat transfer when required and when this has to be augmented by latent heat of evaporation.
  • water is fed into the trough I7 and to such an extent that water is continuously flowing down all the tubes 7 and collected in the gutter 33.
  • the water thus collected can be recirculated after making up losses due to evaporation.
  • FIG. 5 is approximately full scale.
  • the chord length of the tubes being about 37.5 mm. In practice this chord length can vary between 25 mm and mm.
  • the fineness ratio of the tubes as illustrated is at the optimum of about 4: l. A greater fineness ratio of up to 61l will work, but then the liquid capacity of the system may suffer. Smaller ratios up to 2:1 can be used, but then the resistance to air flow becomes bigger.
  • tubes 7 stagger them in rows so that the chord planes of one row is midway between the chord planes in another row as shown in FIG. 4.
  • the cusps and noses of tubes that are in line will in many practical cases be so close together that the boundary layer from the one will slip on to the other behind it without mixing with the balance of the air stream.
  • each tube chord plane is two modules from the chord plane leading it on the right and three chord planes from the chord plane of the tube leading it on the left.
  • every sixth row is a repeat of another row.
  • the cold air stream entering between a pair of leading tubes can be considered as composed of three layers as illustrated in the top part of FIG. 5.
  • the three layers are shown separated by dotted lines and have been marked 41, 42 and 43.
  • a point at the interface between any pair of layers moves more than a row spacing before it comes on to the surface of a trailing tube.
  • a boundary layer slips across a small gap behind a cusp before it again becomes a boundary layer.
  • each tube penetrates be tween pairs of tubes leading it to such an extent that the passages formed have ratios of width to length of 0.3 to 1.0.
  • the dimensions "41 1" are given.
  • the ratio d:l is about 0.3 in the case of the narrower passages and less than l.0 in the case of the wider passages.
  • the passages are all of the same width and the ratio of dsi is about 1.0.
  • aerofoil sections are so chosen that these passages are of substantially constant width along their lengths. in the example of FIG. 5 this means a spacing in the direction of air flow of 25 mm from chord centre to chord centre when the chord length is 37.5 mm.
  • FIGS. 1 to 5 all have smooth sides so that sections taken at any horizontal plane will be the same. lf certain thin gauges of sheet metal are used in making them, they may not be strong enough. In such a case the expedient shown in FIG. 6 may be used.
  • the flanks of a tube 7 are formed with a series of indentations 40 along its length. The indentations all lie within the original aerofoil section and there are no air side protrusions beyond that section.
  • the heat exchanger of the invention is simple to manufacture and easy to assemble. It is expected to be considerably cheaper than conventional heat exchangers of comparable size for the same duty.
  • the tubes are in a plurality of rows parallel to the aperture plane and parallel to one another;
  • each tube is ofa symmetrical aerofoil section with a cuspate trailing edge, with its chord plane normal to the aperture plane, is formed within a continuous aerofoil shape from end to end so that there are no heat transfer surfaces extending into the path of the second fluid, and has a fineness ratio between 6:] and 21l;
  • the tubes are so shaped and rows of tubes are so positioned that the nose of a tube in a trailing row of tubes intercallates between the trailing edges of pairs of tubes in the leading row so that between adjacent trailing and leading tubes passages of substantially constant width along their lengths in the direction of flow of the second fluid are formed:
  • each row is off-set with respect to the row leading it to such an extent that the constant width passage to one side ofa tube is substantially twice the width of the constant width passage to the other side of 2.
  • the heat exchanger claimed in claim 1 in which the tubes are so shaped and positioned that any passage formed where two adjacent tubes are at their closest to one another has a ratio of width between the tubes and length in the direction of flow of the second fluid of between ().3 and L0.
  • each tube is made of sheet metal bent to form the aerofoil shape.
  • each tube sheet is composed of a series of parallel slats parallel to the tube rows and formed with cut-outs to fit around the tubes and a layer of concrete surround ing the tube ends passing through the slats.
  • the heat exchanger claimed in claim 12 including series of spacers positioned at suitable intervals down the lengths of the tubes to effect redistribution of liquid running down the tubesv

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US334215A 1972-03-01 1973-02-21 Heat exchangers Expired - Lifetime US3885936A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US05/535,342 US3969448A (en) 1972-03-01 1974-12-23 Heat exchangers

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ZA721381A ZA721381B (en) 1972-03-01 1972-03-01 Heat exchangers
GB879073A GB1422611A (en) 1972-03-01 1973-02-22 Tubular heat exchangers

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US05/535,342 Division US3969448A (en) 1972-03-01 1974-12-23 Heat exchangers

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US3885936A true US3885936A (en) 1975-05-27

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US334215A Expired - Lifetime US3885936A (en) 1972-03-01 1973-02-21 Heat exchangers

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US (1) US3885936A (enrdf_load_stackoverflow)
AU (1) AU476906B2 (enrdf_load_stackoverflow)
DE (1) DE2309937A1 (enrdf_load_stackoverflow)
FR (1) FR2174218B1 (enrdf_load_stackoverflow)
GB (1) GB1422611A (enrdf_load_stackoverflow)

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3969448A (en) * 1972-03-01 1976-07-13 Basil Gilbert Alfred Lund Heat exchangers
US4067384A (en) * 1976-06-17 1978-01-10 Miyakawa Gene K Heat exchanger core assembly for engine cooling system
US4379485A (en) * 1981-04-09 1983-04-12 Foster Wheeler Energy Corporation Wet/dry steam condenser
US4381817A (en) * 1981-04-27 1983-05-03 Foster Wheeler Energy Corporation Wet/dry steam condenser
US4574868A (en) * 1981-10-02 1986-03-11 Caterpillar Tractor Co. Flow directing element for heat exchanger
US4577684A (en) * 1983-08-12 1986-03-25 Mtu Motoren- Und Turbinen-Union Munchen Gmbh Profiled-tube heat exchanger
US4597436A (en) * 1982-11-19 1986-07-01 Klaus Hagemeister Tubular distributor arrangement for a heat collector vessel
US4632182A (en) * 1982-11-19 1986-12-30 Motoren- Und Turbinen-Union Munchen Gmbh Heat exchanger for gases of greatly different temperatures
US4815535A (en) * 1986-10-29 1989-03-28 Mtu Motoren-Und Turbinen -Union Munchen Gmbh Heat exchanger
FR2696822A1 (fr) * 1992-10-09 1994-04-15 Mtu Muenchen Gmbh Matrice à tubes profilés pour échangeur de chaleur.
US5944094A (en) * 1996-08-30 1999-08-31 The Marley Cooling Tower Company Dry-air-surface heat exchanger
US6178770B1 (en) * 1998-10-22 2001-01-30 Evapco International, Inc. Ice-on-coil thermal storage apparatus and method
US20040035562A1 (en) * 2002-07-12 2004-02-26 Haruyuki Nishijima Heat exchanger for cooling air
EP1235039A3 (en) * 2001-02-23 2004-03-03 Metech S.r.l. Heat exchanger with coil constituted by a tubular element with drop-shaped cross-section
EP1439361A1 (en) * 2003-01-15 2004-07-21 Air Tech. Co., Ltd. Evaporative heat exchanger with a streamline cross section tube coil with less or even without cooling fins
EP1439363A1 (en) * 2003-01-15 2004-07-21 Air Tech. Co., Ltd. Evaporation type condensation radiator piping for refrigeration and air-conditioning facilities
US20050081549A1 (en) * 2003-10-16 2005-04-21 Wu Ho H. Evaporation type condensation radiator piping for refrigeration and air-conditioning facilities
EP1528345A1 (en) 2003-11-03 2005-05-04 Ho-Hsin Wu Evaporative condenser without cooling fins
SG112897A1 (en) * 2003-10-17 2005-07-28 Hsin Wu Ho Evaporation type condensation radiator piping for refrigeration and air-conditioning facilities
US20060231241A1 (en) * 2005-04-18 2006-10-19 Papapanu Steven J Evaporator with aerodynamic first dimples to suppress whistling noise
US20100132921A1 (en) * 2008-12-01 2010-06-03 Daniel Moskal Wake generating solid elements for joule heating or infrared heating
US20130263832A1 (en) * 2012-04-05 2013-10-10 Donald B. Scoggins Fluid Cooling System
US20140130764A1 (en) * 2011-05-05 2014-05-15 Mann + Hummel Gmbh Charge air duct for an internal combustion engine
EP3653984B1 (en) * 2018-11-16 2023-01-25 Hamilton Sundstrand Corporation Plate fin heat exchanger flexible manifold structure
US11686530B2 (en) 2018-03-16 2023-06-27 Hamilton Sundstrand Corporation Plate fin heat exchanger flexible manifold
US20230373031A1 (en) * 2022-05-20 2023-11-23 Hamilton Sundstrand Corporation Additively manufactured heat exchanger with special surface roughness
US11988461B2 (en) 2021-12-13 2024-05-21 Hamilton Sundstrand Corporation Additive airfoil heat exchanger

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FR2337867A1 (fr) * 1976-01-12 1977-08-05 Chausson Usines Sa Echangeur de chaleur a collecteurs epais
US4196157A (en) * 1978-07-06 1980-04-01 Baltimore Aircoil Company, Inc. Evaporative counterflow heat exchange
FR2439967B1 (fr) * 1978-10-23 1985-09-13 Barriquand Perfectionnements apportes aux echangeurs de chaleur
US4755331A (en) 1986-12-02 1988-07-05 Evapco, Inc. Evaporative heat exchanger with elliptical tube coil assembly
BE1003851A3 (fr) * 1990-03-14 1992-06-30 Denis Nicole Plaque tubulaire pour echangeur de chaleur.
RU2123652C1 (ru) * 1994-05-20 1998-12-20 Александр Петрович Капишников Теплообменный элемент
RO115989B1 (ro) * 1998-05-14 2000-08-30 S.C. Romradiatoare S.A. Schimbător de căldură
FR3061953B1 (fr) * 2016-11-03 2019-09-13 Valeo Systemes Thermiques Echangeur thermique et tube associe

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US1422315A (en) * 1919-11-25 1922-07-11 Charles F Spery Radiator for motor vehicles
US2225856A (en) * 1939-12-14 1940-12-24 United Aircraft Corp Heat exchanger
US3111168A (en) * 1954-11-24 1963-11-19 Huet Andre Heat exchangers
US3241609A (en) * 1964-03-03 1966-03-22 Itt Sheet metal heat exchange stack or fire tube for gas fired hot air furnaces

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FR692187A (fr) * 1930-03-17 1930-10-31 économiseur d'air tubulaire
FR748870A (fr) * 1932-04-02 1933-07-12 Chausson Usines Sa échangeur de chaleur perfectionné
FR799978A (fr) * 1935-03-29 1936-06-24 Perfectionnements aux tuyaux à ailettes
FR807796A (fr) * 1936-07-02 1937-01-21 Economiseur Green L Perfectionnements aux faisceaux tubulaires pour échangeurs de chaleur
GB606674A (en) * 1944-08-25 1948-08-18 Sulzer Ag Improvements in or relating to heat-exchangers
US3422884A (en) * 1966-12-28 1969-01-21 Baldwin Lima Hamilton Corp Condenser tube bundles
GB1188981A (en) * 1967-02-01 1970-04-22 Marston Radiators Ltd Methods for Making Heat Exchangers.
FR1544458A (fr) * 1967-11-14 1968-10-31 Air Preheater élément tubulaire pour échangeurs de chaleur
GB1261905A (en) * 1968-06-25 1972-01-26 Atomic Energy Authority Uk Improvements in or relating to tube end plates

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1422315A (en) * 1919-11-25 1922-07-11 Charles F Spery Radiator for motor vehicles
US2225856A (en) * 1939-12-14 1940-12-24 United Aircraft Corp Heat exchanger
US3111168A (en) * 1954-11-24 1963-11-19 Huet Andre Heat exchangers
US3241609A (en) * 1964-03-03 1966-03-22 Itt Sheet metal heat exchange stack or fire tube for gas fired hot air furnaces

Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3969448A (en) * 1972-03-01 1976-07-13 Basil Gilbert Alfred Lund Heat exchangers
US4067384A (en) * 1976-06-17 1978-01-10 Miyakawa Gene K Heat exchanger core assembly for engine cooling system
US4379485A (en) * 1981-04-09 1983-04-12 Foster Wheeler Energy Corporation Wet/dry steam condenser
US4381817A (en) * 1981-04-27 1983-05-03 Foster Wheeler Energy Corporation Wet/dry steam condenser
US4574868A (en) * 1981-10-02 1986-03-11 Caterpillar Tractor Co. Flow directing element for heat exchanger
US4597436A (en) * 1982-11-19 1986-07-01 Klaus Hagemeister Tubular distributor arrangement for a heat collector vessel
US4632182A (en) * 1982-11-19 1986-12-30 Motoren- Und Turbinen-Union Munchen Gmbh Heat exchanger for gases of greatly different temperatures
US4577684A (en) * 1983-08-12 1986-03-25 Mtu Motoren- Und Turbinen-Union Munchen Gmbh Profiled-tube heat exchanger
US4815535A (en) * 1986-10-29 1989-03-28 Mtu Motoren-Und Turbinen -Union Munchen Gmbh Heat exchanger
FR2696822A1 (fr) * 1992-10-09 1994-04-15 Mtu Muenchen Gmbh Matrice à tubes profilés pour échangeur de chaleur.
US5355946A (en) * 1992-10-09 1994-10-18 Mtu Motoren-Und Turbinen-Union Munchen Gmbh Teardrop-shaped heat exchange tube and its process of manufacture
US5944094A (en) * 1996-08-30 1999-08-31 The Marley Cooling Tower Company Dry-air-surface heat exchanger
US6178770B1 (en) * 1998-10-22 2001-01-30 Evapco International, Inc. Ice-on-coil thermal storage apparatus and method
EP1235039A3 (en) * 2001-02-23 2004-03-03 Metech S.r.l. Heat exchanger with coil constituted by a tubular element with drop-shaped cross-section
US20040035562A1 (en) * 2002-07-12 2004-02-26 Haruyuki Nishijima Heat exchanger for cooling air
EP1439363A1 (en) * 2003-01-15 2004-07-21 Air Tech. Co., Ltd. Evaporation type condensation radiator piping for refrigeration and air-conditioning facilities
EP1439361A1 (en) * 2003-01-15 2004-07-21 Air Tech. Co., Ltd. Evaporative heat exchanger with a streamline cross section tube coil with less or even without cooling fins
US20050081549A1 (en) * 2003-10-16 2005-04-21 Wu Ho H. Evaporation type condensation radiator piping for refrigeration and air-conditioning facilities
SG112897A1 (en) * 2003-10-17 2005-07-28 Hsin Wu Ho Evaporation type condensation radiator piping for refrigeration and air-conditioning facilities
EP1528345A1 (en) 2003-11-03 2005-05-04 Ho-Hsin Wu Evaporative condenser without cooling fins
US20060231241A1 (en) * 2005-04-18 2006-10-19 Papapanu Steven J Evaporator with aerodynamic first dimples to suppress whistling noise
US20100132921A1 (en) * 2008-12-01 2010-06-03 Daniel Moskal Wake generating solid elements for joule heating or infrared heating
US8541721B2 (en) 2008-12-01 2013-09-24 Daniel Moskal Wake generating solid elements for joule heating or infrared heating
US20140130764A1 (en) * 2011-05-05 2014-05-15 Mann + Hummel Gmbh Charge air duct for an internal combustion engine
US20130263832A1 (en) * 2012-04-05 2013-10-10 Donald B. Scoggins Fluid Cooling System
US9151250B2 (en) * 2012-04-05 2015-10-06 Donald B. Scoggins Fluid cooling system
US11686530B2 (en) 2018-03-16 2023-06-27 Hamilton Sundstrand Corporation Plate fin heat exchanger flexible manifold
US12379163B2 (en) 2018-03-16 2025-08-05 Hamilton Sundstrand Corporation Plate fin heat exchanger flexible manifold
EP3653984B1 (en) * 2018-11-16 2023-01-25 Hamilton Sundstrand Corporation Plate fin heat exchanger flexible manifold structure
US11988461B2 (en) 2021-12-13 2024-05-21 Hamilton Sundstrand Corporation Additive airfoil heat exchanger
US20230373031A1 (en) * 2022-05-20 2023-11-23 Hamilton Sundstrand Corporation Additively manufactured heat exchanger with special surface roughness
US12275089B2 (en) * 2022-05-20 2025-04-15 Hamilton Sundstrand Corporation Additively manufactured heat exchanger with special surface roughness

Also Published As

Publication number Publication date
AU476906B2 (en) 1976-10-07
FR2174218B1 (enrdf_load_stackoverflow) 1978-03-03
AU5256073A (en) 1974-08-29
DE2309937A1 (de) 1973-09-13
GB1422611A (en) 1976-01-28
FR2174218A1 (enrdf_load_stackoverflow) 1973-10-12

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